US3924598A - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
US3924598A
US3924598A US302692A US30269272A US3924598A US 3924598 A US3924598 A US 3924598A US 302692 A US302692 A US 302692A US 30269272 A US30269272 A US 30269272A US 3924598 A US3924598 A US 3924598A
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United States
Prior art keywords
fuel
charge
pilot
control means
providing
Prior art date
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Expired - Lifetime
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US302692A
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English (en)
Inventor
Charles W Davis
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Texaco Inc
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Texaco Inc
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Filing date
Publication date
Application filed by Texaco Inc filed Critical Texaco Inc
Priority to US302692A priority Critical patent/US3924598A/en
Priority to GB4251773A priority patent/GB1437447A/en
Priority to NL7312808A priority patent/NL7312808A/xx
Priority to JP48105086A priority patent/JPS5047035A/ja
Priority to AU60526/73A priority patent/AU479123B2/en
Priority to CA181,897A priority patent/CA1015625A/en
Priority to FR7336195A priority patent/FR2205102A5/fr
Priority to IT30542/73A priority patent/IT1019555B/it
Priority to BR8364/73A priority patent/BR7308364D0/pt
Priority to DE19732353981 priority patent/DE2353981A1/de
Priority to ES420068A priority patent/ES420068A1/es
Priority to CH1531973A priority patent/CH578118A5/xx
Priority to SU731966303A priority patent/SU648131A3/ru
Priority to PL1973166236A priority patent/PL95066B1/pl
Publication of USB302692I5 publication Critical patent/USB302692I5/en
Application granted granted Critical
Publication of US3924598A publication Critical patent/US3924598A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/046—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into both the combustion chamber and the intake conduit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/12—Engines characterised by fuel-air mixture compression with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
    • F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
    • F02D41/3023—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the stratified charge spark-ignited mode
    • F02D41/3029—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the stratified charge spark-ignited mode further comprising a homogeneous charge spark-ignited mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
    • F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
    • F02D41/3035—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode
    • F02D41/3041—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode with means for triggering compression ignition, e.g. spark plug
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3094—Controlling fuel injection the fuel injection being effected by at least two different injectors, e.g. one in the intake manifold and one in the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/044—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the intake conduit downstream of an air throttle valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/045—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/42—Texaco combustion process
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
    • F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
    • F02D41/3035—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode
    • F02D41/3041—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode with means for triggering compression ignition, e.g. spark plug
    • F02D41/3047—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode with means for triggering compression ignition, e.g. spark plug said means being a secondary injection of fuel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/40—Engine management systems

Definitions

  • ABSTRACT A method and apparatus for operating a premixed charge, piston type, internal combustion engine with variation of the premixed charge to a leaner fuel-air mixture than is usual, wherein ignition of the main, power producing, premixed fuel-air mixture charge is caused by the flame resulting from spark ignition of a pilot fuel charge which is injected into a swirling mixture adjacent positive ignition means in the engine cylinder.
  • the direct ignition method requires intake throttling for load control becuase the mixture strength must be maintained above the lean limit of spark ignition.
  • This lean limit usually occurs at a fuel to air (F/A) ratio of about 0.055 (weight basis) depending on the engine.
  • F/A ratio is maintained generally in the range of from 0.06 to 0.08. If the engine were to run without intake throttling, it would have to function with a F/A ratio of about 0.005 to provide zero brake output or idle operation.
  • the intake throttling required with direct spark igintion causes a severe reduction in the part load fuel economy of the engine.
  • a premixed charge, internal combustion engine with a compression ignition pilot flame eliminates the need for throttling in most instances, because considerably leaner mixtures can be ignited by a flame than by a direct spark.
  • the output of such engines therefore is regulated generally by variation of mixture strength without air throttling, and part load fuel economy is much better than with direct spark ignition engines.
  • compression ignition of the pilot charge requires a relatively high compression ratio and a high Cotane number pilot fuel.
  • the high compression ratio is to some degree incompatible with the compression ratio restriction imposed by possible detonation of the main premixed charge depending on its Octane number rating and by anti-pollution requirements.
  • two distinctly different types of fuel must be available: high Cotane fuel for the pilot charge and high Octane fuel for the premixed charge, and the engine must be rugged to accommodate the necessarily high compression ratio.
  • non-throttled premixed charge engines that use variable mixture strength is limited to those mixtures which are sufficiently fuel rich to support flame propagation. Operation below the lean limit of flame propagation is impossible regardless of the method of ignition. For the purposes of this specification, it is known that this lean limit corresponds to a F/A ratio of about b (LOW-0.020, although the actual lean limit may be somewhat leaner or richer depending on the particular engine in question. Engine output using an unthrottled mixture of this strength usually will be greater than the minimum output desired, and special means to provide stable operation with a further reduction of total fuel supplied to the engine must be used for lighter loads.
  • This invention relates to an improved method and apparatus for the operation of a premixed charge, piston type, internal combustion engine. It relates particularly to extending the operation of such an engine to very lean fuel to air (F/A) mixtures by variation of the mix ture strength of the premixed charge, resulting in low fuel consumption, production of low exhaust emissions and low exhaust gas temperatues. Ignition of such mix- 2 tures is caused by the flame of a spark ignitably rich pilot fuel charge.
  • F/A fuel to air
  • the pilot fuel charge is injected into a cylinder toward positive ignition means, e.g., a spark plug.
  • the pilot fuel charge then is ignited in the same non-knocking manner as disclosed in US. Pat. Nos. 2,484,009, 2,864,347, 2,958,314 and 3,094,974.
  • the resulting pilot fuel charge flame ingites the main, power producing, premixed fuel charge.
  • FIG. ll shows diagrammatically a cylinder of an internal combustion engine, and the basic structural elements for the injection of the pilot fuel charge and for the admission of the premixed fuel/air charge;
  • FIG. 2 is a partial cross section taken along line 2-2 of FIG. I, with an additional showing of the structures for the provision of the pilot and premixed charges;
  • FIGS. 3 and 4 are graphs illustrating fuel supply and air flow schedules with variations of engine output at constant engine speeds
  • FIGS. 5 and 6 disclose apparatus for the coordinated control of pilot injection quantity, the premixed charge fuel quantity and the intake air throttling with variation of engine output at very low loads;
  • FIG. 7 illustrates diagrammatically the application of the invention to a two-stroke cycle, internal combustion engine.
  • FIGS. 1 and 2 illustrate a single cylinder, internal combustion engine structure, operating on a fourstroke cycle, disclosing the several features of this invention.
  • a pilot fuel injection nozzle 1 is mounted in the wall of the engine cylinder CY so that fuel can be introduced into the combustion chamber CC of the cylinder at a point immediately adjacent positive ignition means, e. g., spark plug 2.
  • Nozzle 1 is connected to fuel supply source 3 via pilot fuel pump and control means 4, the latter providing intermittent, timed injection of a predeterminted quantitiy of pilot fuel, which may be constant.
  • the timing of this fuel injection selected as desired, usually ranges from about 0 to 40 crank angle degrees BTC on the compression stroke of the engine cycle.
  • Spark plug 2 is connected in the normal manner to ignition system 5, the firing of which is coordinated for a spark to occur at the spark plug gap at substantially the same time that pilot fuel injection begins, so that the desired pilot flame is produced. This procedure is described fully in US. Pat. No. 2,484,009, issued to EM. Barber, the disclosure of which is incorporated herein by this reference.
  • a variable strength premixed charge is supplied to the combustion chamber of the engine cylinder via the intake tube 6 and the intake valve I.
  • Fuel flow is varied in proportion to load from substantially zero to the quantity required to provide an unthrottled premixed charge with a F/A ratio of 0.08. Air flow is unthrottled except as noted later, depending on the desired engine output.
  • Nozzle 7, control 8 and throttle valve 9 comprise one means for producing the desired amount and mixture strength of the premixed charge.
  • the inlet port and valve are disposed so that the incoming premixed charge swirls about the axis of the combustion chamber CC at about 3 times the rate of engine crankshaft rotation. This premixed charge is ignited by the pilot flame.
  • FIG. 1 also discloses an alternate location for the premixed charge nozzle at 70, mounted to discharge into the combustion chamber of the cylider. Intermittent timed injection must be used with this location with injection timed to occur early in the intake stroke.
  • the fuel used by the engine can be a liquid or a gas with appropriate variations of pumping and control means 4 and 8, such means being known in the art.
  • pilot injection nozzle 1 injects the normal pilot fuel charge, which consists of from to 15 percent of the full load premixed fuel charge, into the combustion chamber where it is ignited by a spark at spark plug 2 in essentially the same manner as in the non-knocking combustion process as disclosed in the above cited U.S. Pat. No. 2,484,009.
  • the flame resulting from combustion of the pilot fuel charge ignites the main premixed charge and the en gine develops the required power output.
  • pilot injection When the engine output is such that the premixed charge mixture strength exceeds about 0.055 F/A ratio, it may be desirable to terminate pilot injection since the premixed charge now can be spark ignited directly. Continuation of pilot injection may be desirable also in some cases since improved ignition will be assured thereby.
  • FIGS. 3 and 4 illustrate generally the fuel supply and air flow schedules provided with variations of engine output according to the operations described above.
  • FIGS. 5 and 6 disclose means for obtaining this coordinated control of the pilot injection quantity, the premixed charge fuel quantity and the intake air throttling with variation of engine output.
  • the control shaft 10 of premixed charge fuel control unit 8 is equipped with arm 12 which is attached to the main control lever 14 by pinned link 16.
  • Control lever 14 is pivotally mounted at point 15 and is positioned manually or by a governor (not shown).
  • Pilot charge fuel control unit 4 has control shaft 11 equipped with arm 13 which is attached to control lever 14 by slotted, pinned link 17.
  • Arm 13 is also connected to solenoid 20 by slotted solenoid armature 21 via pin 22.
  • the pilot charge is at its normal value and the premixed charge F/A ratio at about 0.04. If the control arm 14 is moved toward the maximum engine output position, link 16 and arm 12 will cause the premixed fuel delivery to be increased. The pilot fuel quantity will remain constant because of slotted link 17 until a premixed charge F/A ratio of about 0.055 is reached (note that the throttle valve 9 is wide open), at which point arm 12 will contact electrical switch 23, energizing solenoid 20 and causing control arm 13 to be pulled to the off position terminating pilot injection.
  • switch 23, solenoid 20 and solenoid armature 21 may be omitted so that pilot injection is not terminated when the premixed fuel-air ratio has increased to 0.055. If the mechanism is moved from a position where the premixed charge is richer than 0.055 F/A ratio to one where itis leaner, the reverse situation will occur; arm 12 will trip switch 23, deenergi'zing solenoid 20, so that spring 19 can push arm 13 to the position where normal pilot injection is restored.
  • FIG. 5 which shows the arrangement for light load control by variation of pilot injection quantity
  • control lever 14 if control lever 14 is moved toward the off position, the premixed charge fuel flow will be reduced until the unthrottled F/A ratio reaches about 0.015, at which point arm 12 will trip electrical switch 26, energizing a solenoid valve (not shown) in the fuel supply line to nozzle 7 ,and terminating fuel delivery therefrom.
  • the pilot charge fuel will be maintained at its normal value because of the slotted connection between member 13 and 17.
  • pilot fuel flow will increase until arm 12 trips switch 26, at which point pilot fuel flow will be returned to its normal amount and premixed fuel flow will be restored with a F/A ratio of about 0.015.
  • Spring 35 urges member 18 toward arm 13, spring 35 being stronger than spring 19.
  • throttle valve 9 pivots on shaft 27 in mixing tube 6, with the shaft being equipped with arm 28, which is connected to control lever 14 by slotted link 29. Throttle arm 28 is held against stop 32 in the wide open position by spring 31. If the control lever 14 is moved toward the off position, premixed charge fuel is reduced by the action of members 16 and 12 but pilot fuel flow is maintained at a maximum because of the slot in link 17. When control lever 14 has reached the point where the unthrottled premixed charge F/A ratio has been reduced to' about 0.0 l 5, pin 30 in arm 28 engages the end of the slot in link 29.
  • control lever 14 Further motion of control lever 14 toward the off position results in a progressive closure of throttle valve 9 and a further reduction of the premixed charge fuel flow, maintaining the premixed F/A ratio above about 0.015 and therefore capable of sustaining flame propagation.
  • throttle valve 9 has been substantially closed and the premixed fuel flow is substantially zero, pin 25 in arm 13 engages the end of the slot in link 17 and a slight further movement of control lever 14 to the off position causes pilot fuel to be reduced abruptly from its normal value to zero. Note that in all cases, the normal quantity of pilot fuel supplied is that which is required by the engine to operate at zero brake output.
  • the disclosure has been directed generally to a four-stroke cycle, internal combustion engine with the fuel for the premixed charge introduced into the air in the intake tube (manifold) external the engine cylinder.
  • Application of the invention to cylinder injection of the fuel which will form the premixed charge is illustrated alternatively in FIG. 1 also, substituting the dashed line and the nozzle 7a for the nozzle 7 and the solid line leading from control 8 to it.
  • Nozzle 7a must have intermittent injection timed to occur on the early part of the compression stroke, and is to follow a fuel quantity program similar to that illustrated by FIG. 3 and discussed in detail in connection with nozzle 7.
  • FIG. 7 shows a schematic diagram of a two-stroke cycle, piston ported intake, poppet exhaust, uniflow engine cylinder having angled intake ports to produce swirl.
  • the cylinder is equipped with conventional engine driven and/or exhaust driven air blower means generally designated as 36.
  • Other components of the engine have the same numerical designations and serve the same purposes as previously described with respect to FIGS. 1 and 2.
  • Nozzle 7' of the 2-cycle drawing, FIG. 7, injects fuel for the premixed charge which is ignited by the inflamed pilot charge, and must have intermittent injection timed to start near the exhaust and intake closings and to terminate before the beginning of the pilot injection.
  • the nozzle 7 is to follow a fuel quantity program similar to that illustrated by FIG. 3 and, of course, based on the air trapped in the cylinder.
  • nozzle 7" injects fuel for the premixed charge which is ignited by the inflamed pilot charge.
  • Nozzle 7" may have continuous fuel flow fol lowing a pattern similar to that illustrated by FIGS. 3 or 4 based on the air supplied to the cylinder. This alternate position nozzle is in an undesirable location since part of the mixture which it forms will pass directly through the engine cylinder.
  • the subject disclosure may be applied also to rotary combustion chamber, internal combustion engines which have a substantially triangular rotating piston revolving in an epitrochoidal chamber of generally rect angular shape to drive a crankshaft (not shown).
  • An apparatus for the coordinated control of the operation of an internal combustion engine with a leaner usual fuel-air mixture, i.e., a fuel to air (F/A) ratio less than 0.055 (weight basis), by variation of the mixture strength with maximum air consumption comprising a first control means comprising a pilot charge fuel control unit and including injection means for pro viding an intermittent timed injection of a predetermined quantity of a pilot fuel charge into the combus tion chamber of a cylinder of said engine and positive ignition means, e.g.
  • a spark plug in said combustion chamber adjacent said injection means, intake means for providing a variable premixed fuel-air mixture leading into, said combustion chamber a second control means comprising a premixed charge fuel control unit and including a nozzle positioned in said intake means for providing fuel thereinto, a first pivoted triple linkage comprising an arm, a pinned link and a control lever in operative association with said second control means and electrical switch means actuated thereby, a second triple linkage comprising an arm and a pair of slotted links pinned thereto in operative association with said first control means, one of said pair of slotted links being joined pivotally to said control lever of said first triple linkage, said pair of slotted links responding to the positioning of said control lever of said first triple linkage, one of said pair of slotted links of said second triple linkage being responsive to said electrical switch means.
  • a linkage comprising a slotted link pivotally joined to said control lever of said first pivoted linkage and an arm pivoted to said throttle valve for controlling intake air with variation of engine output at very low loads by actuation of said control lever.
  • the pilot fuel charge control means providing for a constant quantity for a predetermined time.
  • pilot fuel charge control means providing sufficient fuel to form a fuel-air mixture capable of ignition by said positive means.
  • said second control means providing a fuel to air mixture for flame ignition thereof.
  • said second control means providing a fuel to air mixture ratio in the range from about 0.015 to about 0.080.
  • said second control means providing a constant quantity of pilot fuel
  • said first control means controlling air consumption including a throttle valve for very low load operation below a fuel to air ratio of 0.015.
  • said pilot fuel charge providing said constant quantity until 0.055 F/A of unthrottled premixed fuel is reached.
  • said second control means continuously providing pilot fuel throughout the engine load range.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Fuel-Injection Apparatus (AREA)
US302692A 1972-11-01 1972-11-01 Internal combustion engine Expired - Lifetime US3924598A (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US302692A US3924598A (en) 1972-11-01 1972-11-01 Internal combustion engine
GB4251773A GB1437447A (en) 1972-11-01 1973-09-10 Internal combustion engine
NL7312808A NL7312808A (US07696358-20100413-C00002.png) 1972-11-01 1973-09-18
JP48105086A JPS5047035A (US07696358-20100413-C00002.png) 1972-11-01 1973-09-19
AU60526/73A AU479123B2 (en) 1972-11-01 1973-09-20 Internal combustion engine
CA181,897A CA1015625A (en) 1972-11-01 1973-09-25 Internal combustion engine
FR7336195A FR2205102A5 (US07696358-20100413-C00002.png) 1972-11-01 1973-10-10
IT30542/73A IT1019555B (it) 1972-11-01 1973-10-24 Apparecchiatura per l alimentazione del combustibile nei motori endotermici
BR8364/73A BR7308364D0 (pt) 1972-11-01 1973-10-25 Motor de combustao interna
DE19732353981 DE2353981A1 (de) 1972-11-01 1973-10-27 Verfahren und vorrichtung zum betreiben einer verbrennungskraftmaschine
ES420068A ES420068A1 (es) 1972-11-01 1973-10-29 Metodo de accionamiento de un motor de combustion interna.
CH1531973A CH578118A5 (US07696358-20100413-C00002.png) 1972-11-01 1973-10-31
SU731966303A SU648131A3 (ru) 1972-11-01 1973-10-31 Способ работы двигател внутреннего сгорани
PL1973166236A PL95066B1 (US07696358-20100413-C00002.png) 1972-11-01 1973-10-31

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US302692A US3924598A (en) 1972-11-01 1972-11-01 Internal combustion engine

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Publication Number Publication Date
USB302692I5 USB302692I5 (US07696358-20100413-C00002.png) 1975-01-28
US3924598A true US3924598A (en) 1975-12-09

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US302692A Expired - Lifetime US3924598A (en) 1972-11-01 1972-11-01 Internal combustion engine

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Cited By (36)

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US4080949A (en) * 1974-08-21 1978-03-28 Holec N.V. Combustion engine and injector for a combustion engine
US4119066A (en) * 1975-06-20 1978-10-10 Daimler-Benz Aktiengesellschaft Internal combustion engine
US4188923A (en) * 1977-02-24 1980-02-19 Regie Nationale Des Usines Renault Internal combustion engine fuel feed
US4254741A (en) * 1978-11-13 1981-03-10 The Dow Chemical Company Diesel engine with dual fuel injection system and method of operation
US4414940A (en) * 1981-04-13 1983-11-15 Loyd Robert W Conditioned compression ignition system for stratified charge engines
US4621599A (en) * 1983-12-13 1986-11-11 Nippon Soken, Inc. Method and apparatus for operating direct injection type internal combustion engine
US4815422A (en) * 1974-12-24 1989-03-28 Josef Schaich Four stroke piston engine
US4938213A (en) * 1988-04-26 1990-07-03 Toyota Jidosha Dabushiki Kaisha Two-stroke engine
US4955339A (en) * 1988-11-18 1990-09-11 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US5052360A (en) * 1989-12-21 1991-10-01 Gas Research Institute Process and apparatus for timed port injection of fuel to form a stratified charge
US5119780A (en) * 1991-06-11 1992-06-09 Southwest Research Institute Staged direct injection diesel engine
US5168839A (en) * 1990-06-01 1992-12-08 Mazda Motor Corporation Engine induction system
US5181493A (en) * 1990-05-25 1993-01-26 Yamaha Hatsudoki Kabushiki Kaisha Operation control device for in-cylinder injection engine
US5291865A (en) * 1991-09-13 1994-03-08 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US5443045A (en) * 1992-04-24 1995-08-22 Bimota, S.P.A. Two-stroke fuel-injected internal combustion engine
US5605127A (en) * 1994-05-27 1997-02-25 Mitsubishi Jukogyo Kabushiki Kaisha Cylinder cover for diesel engine
AT2489U1 (de) * 1997-11-20 1998-11-25 Avl List Gmbh Hubkolbenbrennkraftmaschine mit fremdzündung
US6032640A (en) * 1998-10-02 2000-03-07 The University Of British Columbia Control method for spark-ignition engines
US6253729B1 (en) * 1997-04-30 2001-07-03 Yamaha Hatsudoki Kabushiki Kaisha Induction control for direct injected engine
US6289877B1 (en) * 1998-04-29 2001-09-18 Anr Pipeline Co. Method and system for controlling an air-to-fuel ratio in a non-stoichiometric power governed gaseous-fueled stationary internal combustion engine
US6314940B1 (en) * 1999-03-23 2001-11-13 Daimlerchrysler Ag Fuel feed system for a spark-ignition internal combustion engine and a method of operating such an internal combustion engine
WO2001086127A2 (en) * 2000-05-08 2001-11-15 Cummins, Inc. Internal combustion engine operable in pcci mode with post-ignition injection and method of operation
US6499463B1 (en) * 2001-07-20 2002-12-31 Kleenair Systems, Inc. Dual fuel source diesel engine
US20030113213A1 (en) * 2001-11-02 2003-06-19 Georg Chekaiban Method and system for controlling a cooling system of an internal-combustion engine
US6637404B2 (en) * 2001-09-28 2003-10-28 Avl List Gmbh Method for controlling the operation of an internal combustion engine
US20050155344A1 (en) * 2002-07-04 2005-07-21 Toyota Jidosha Kabushiki Kaisha Internal combustion engine of compressing and auto-igniting air-fuel mixture and method of controlling such internal combustion engine
CN1304739C (zh) * 2001-07-20 2007-03-14 克林空气系统公司 双燃料源的柴油机
DE10120486B4 (de) * 2000-04-28 2007-10-11 Avl List Gmbh Verfahren zum Betreiben einer fremdgezündeten direkteinspritzenden Brennkraftmaschine
US20080196690A1 (en) * 2006-11-28 2008-08-21 Isamu Hotta Internal combustion engine with auxiliary combustion chamber
DE19815266B4 (de) * 1997-04-16 2008-09-18 Volkswagen Ag Verfahren zur Einspritzung von Kraftstoff in eine Brennkraftmaschine
US20080236546A1 (en) * 2007-03-27 2008-10-02 Nissan Motor Co., Ltd. Combustion control system for internal combustion engine
US20080319635A1 (en) * 2007-06-20 2008-12-25 Ford Global Technologies, Llc Internal combustion engine system, and a method in such an engine system
US20140116392A1 (en) * 2012-10-31 2014-05-01 Electro-Motive Diesel, Inc. Fuel system for a dual-fuel engine
US20140116386A1 (en) * 2012-10-31 2014-05-01 Electro-Motive Diesel Inc Fuel system having multiple gaseous fuel injectors
EP2781731A4 (en) * 2011-09-29 2015-12-23 Corona José María Beltran FUEL INJECTION CONTROL AND STRATEGIES THEREFOR
EP3095981A1 (en) * 2015-05-22 2016-11-23 Caterpillar Motoren GmbH & Co. KG Counter flow ignition in internal combustion engines

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JPS58102738U (ja) * 1981-12-29 1983-07-13 日産ディーゼル工業株式会社 デイ−ゼルエンジンの騒音低減装置
GB8500270D0 (en) * 1985-01-05 1985-02-13 Greenhough J H Four stroke i c engine
DE19515781A1 (de) * 1995-04-28 1996-10-31 Ficht Gmbh Verfahren und Vorrichtung zur Ladungsschichtung bei Ottomotoren
DE19704640B4 (de) * 1997-02-07 2008-10-23 Audi Ag Verfahren zum Betreiben einer flammgezündeten Brennkraftmaschine
AT1922U3 (de) * 1997-03-14 1998-06-25 Avl List Gmbh Verfahren zur einbringung von kraftstoff in den brennraum einer direkteinspritzenden otto-brennkraftmaschine
DE19801245C2 (de) * 1998-01-15 2000-12-14 Andresen Peter L Anordnung zur Beladung eines Brennraumes über eine mehrfach öffnende Ventilkombination
FR2921692A1 (fr) * 2007-09-27 2009-04-03 Inst Francais Du Petrole Procede de controle de la combustion pour un moteur a combustion interne utilisant un combustible du type gaz naturel

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US2184357A (en) * 1938-05-04 1939-12-26 Mallory Marion Internal combustion engine
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Cited By (62)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4080949A (en) * 1974-08-21 1978-03-28 Holec N.V. Combustion engine and injector for a combustion engine
US4815422A (en) * 1974-12-24 1989-03-28 Josef Schaich Four stroke piston engine
US4119066A (en) * 1975-06-20 1978-10-10 Daimler-Benz Aktiengesellschaft Internal combustion engine
US4188923A (en) * 1977-02-24 1980-02-19 Regie Nationale Des Usines Renault Internal combustion engine fuel feed
US4254741A (en) * 1978-11-13 1981-03-10 The Dow Chemical Company Diesel engine with dual fuel injection system and method of operation
US4414940A (en) * 1981-04-13 1983-11-15 Loyd Robert W Conditioned compression ignition system for stratified charge engines
US4621599A (en) * 1983-12-13 1986-11-11 Nippon Soken, Inc. Method and apparatus for operating direct injection type internal combustion engine
US4938213A (en) * 1988-04-26 1990-07-03 Toyota Jidosha Dabushiki Kaisha Two-stroke engine
US4955339A (en) * 1988-11-18 1990-09-11 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US5052360A (en) * 1989-12-21 1991-10-01 Gas Research Institute Process and apparatus for timed port injection of fuel to form a stratified charge
US5181493A (en) * 1990-05-25 1993-01-26 Yamaha Hatsudoki Kabushiki Kaisha Operation control device for in-cylinder injection engine
US5168839A (en) * 1990-06-01 1992-12-08 Mazda Motor Corporation Engine induction system
US5119780A (en) * 1991-06-11 1992-06-09 Southwest Research Institute Staged direct injection diesel engine
US5291865A (en) * 1991-09-13 1994-03-08 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
US5357925A (en) * 1991-09-13 1994-10-25 Toyota Jidosha Kabushika Kaisha Internal combustion engine
US5443045A (en) * 1992-04-24 1995-08-22 Bimota, S.P.A. Two-stroke fuel-injected internal combustion engine
US5605127A (en) * 1994-05-27 1997-02-25 Mitsubishi Jukogyo Kabushiki Kaisha Cylinder cover for diesel engine
DE19815266B4 (de) * 1997-04-16 2008-09-18 Volkswagen Ag Verfahren zur Einspritzung von Kraftstoff in eine Brennkraftmaschine
US6253729B1 (en) * 1997-04-30 2001-07-03 Yamaha Hatsudoki Kabushiki Kaisha Induction control for direct injected engine
AT2489U1 (de) * 1997-11-20 1998-11-25 Avl List Gmbh Hubkolbenbrennkraftmaschine mit fremdzündung
US6289877B1 (en) * 1998-04-29 2001-09-18 Anr Pipeline Co. Method and system for controlling an air-to-fuel ratio in a non-stoichiometric power governed gaseous-fueled stationary internal combustion engine
US6032640A (en) * 1998-10-02 2000-03-07 The University Of British Columbia Control method for spark-ignition engines
US6314940B1 (en) * 1999-03-23 2001-11-13 Daimlerchrysler Ag Fuel feed system for a spark-ignition internal combustion engine and a method of operating such an internal combustion engine
DE10120486B4 (de) * 2000-04-28 2007-10-11 Avl List Gmbh Verfahren zum Betreiben einer fremdgezündeten direkteinspritzenden Brennkraftmaschine
US6516774B2 (en) 2000-05-08 2003-02-11 Cummins Inc. Premixed charge compression ignition engine with variable speed SOC control and method of operation
DE10191817B4 (de) * 2000-05-08 2008-08-28 Cummins, Inc., Columbus Mehrbetriebsmodus-Motor und Betriebsverfahren
WO2001086126A3 (en) * 2000-05-08 2002-03-28 Cummins Inc Multiple operating mode engine and method of operation
WO2001086127A3 (en) * 2000-05-08 2002-03-28 Cummins Inc Internal combustion engine operable in pcci mode with post-ignition injection and method of operation
WO2001086126A2 (en) * 2000-05-08 2001-11-15 Cummins, Inc. Multiple operating mode engine and method of operation
GB2370316B (en) * 2000-05-08 2004-08-25 Cummins Inc Premixed charge compression ignition engine with variable speed soc control and method of operation
WO2001086127A2 (en) * 2000-05-08 2001-11-15 Cummins, Inc. Internal combustion engine operable in pcci mode with post-ignition injection and method of operation
WO2001086125A3 (en) * 2000-05-08 2002-03-21 Cummins Inc Premixed charge compression ignition engine with variable speed soc control and method of operation
US6561157B2 (en) 2000-05-08 2003-05-13 Cummins Inc. Multiple operating mode engine and method of operation
WO2001086125A2 (en) * 2000-05-08 2001-11-15 Cummins, Inc. Premixed charge compression ignition engine with variable speed soc control and method of operation
US6907870B2 (en) 2000-05-08 2005-06-21 Cummins Inc. Multiple operating mode engine and method of operation
US6684849B2 (en) 2000-05-08 2004-02-03 Cummins Inc. Multiple operating mode engine and method of operation
US6684852B2 (en) 2000-05-08 2004-02-03 Cummins Inc. Internal combustion engine operable in PCCI mode with post-ignition injection and method of operation
US20040149255A1 (en) * 2000-05-08 2004-08-05 Cummins Inc. Multiple operating mode engine and method of operation
GB2369159B (en) * 2000-05-08 2004-09-01 Cummins Inc Internal combustion engine operable in pcci mode with post-ignition injection and method of operation
WO2003008776A2 (en) * 2001-07-20 2003-01-30 Kleenair Systems, Inc. Dual fuel source diesel engine
US6499463B1 (en) * 2001-07-20 2002-12-31 Kleenair Systems, Inc. Dual fuel source diesel engine
WO2003008776A3 (en) * 2001-07-20 2003-03-13 Kleenair Systems Inc Dual fuel source diesel engine
CN1304739C (zh) * 2001-07-20 2007-03-14 克林空气系统公司 双燃料源的柴油机
US6637404B2 (en) * 2001-09-28 2003-10-28 Avl List Gmbh Method for controlling the operation of an internal combustion engine
US6772716B2 (en) * 2001-11-02 2004-08-10 Bayerische Motoren Werke Aktiengesellschaft Method and system for controlling a cooling system of an internal-combustion engine
US20030113213A1 (en) * 2001-11-02 2003-06-19 Georg Chekaiban Method and system for controlling a cooling system of an internal-combustion engine
US7188607B2 (en) * 2002-07-04 2007-03-13 Toyota Jidosha Kabushiki Kaisha Internal combustion engine of compressing and auto-igniting air-fuel mixture and method of controlling such internal combustion engine
US20050155344A1 (en) * 2002-07-04 2005-07-21 Toyota Jidosha Kabushiki Kaisha Internal combustion engine of compressing and auto-igniting air-fuel mixture and method of controlling such internal combustion engine
US7320302B2 (en) 2002-07-04 2008-01-22 Toyota Jidosha Kabushiki Kaisha Internal combustion engine of compressing and auto-igniting air-fuel mixture and method of controlling such internal combustion engine
US20070039588A1 (en) * 2002-07-04 2007-02-22 Toyota Jidosha Kabushiki Kaisha Internal combustion engine of compressing and auto-igniting air-fuel mixture and method of controlling such internal combustion engine
US7814883B2 (en) * 2006-11-28 2010-10-19 Nissan Motor Co., Ltd. Internal combustion engine with auxiliary combustion chamber
US20080196690A1 (en) * 2006-11-28 2008-08-21 Isamu Hotta Internal combustion engine with auxiliary combustion chamber
US20080236546A1 (en) * 2007-03-27 2008-10-02 Nissan Motor Co., Ltd. Combustion control system for internal combustion engine
US7721703B2 (en) * 2007-03-27 2010-05-25 Nissan Motor Co., Ltd. Combustion control system for internal combustion engine
US20080319635A1 (en) * 2007-06-20 2008-12-25 Ford Global Technologies, Llc Internal combustion engine system, and a method in such an engine system
US7644696B2 (en) * 2007-06-20 2010-01-12 Ford Global Technologies, Llc Internal combustion engine system, and a method in such an engine system
EP2781731A4 (en) * 2011-09-29 2015-12-23 Corona José María Beltran FUEL INJECTION CONTROL AND STRATEGIES THEREFOR
US20140116392A1 (en) * 2012-10-31 2014-05-01 Electro-Motive Diesel, Inc. Fuel system for a dual-fuel engine
US20140116386A1 (en) * 2012-10-31 2014-05-01 Electro-Motive Diesel Inc Fuel system having multiple gaseous fuel injectors
US9046068B2 (en) * 2012-10-31 2015-06-02 Electro-Motive Diesel, Inc. Fuel system for a dual-fuel engine
US9188085B2 (en) * 2012-10-31 2015-11-17 Electro-Motive Diesel, Inc. Fuel system having multiple gaseous fuel injectors
EP3095981A1 (en) * 2015-05-22 2016-11-23 Caterpillar Motoren GmbH & Co. KG Counter flow ignition in internal combustion engines

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IT1019555B (it) 1977-11-30
USB302692I5 (US07696358-20100413-C00002.png) 1975-01-28
CH578118A5 (US07696358-20100413-C00002.png) 1976-07-30
ES420068A1 (es) 1976-03-01
NL7312808A (US07696358-20100413-C00002.png) 1974-05-03
BR7308364D0 (pt) 1974-08-15
PL95066B1 (US07696358-20100413-C00002.png) 1977-09-30
SU648131A3 (ru) 1979-02-15
CA1015625A (en) 1977-08-16
GB1437447A (en) 1976-05-26
AU6052673A (en) 1975-03-20
DE2353981A1 (de) 1974-05-09
JPS5047035A (US07696358-20100413-C00002.png) 1975-04-26
FR2205102A5 (US07696358-20100413-C00002.png) 1974-05-24

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